EP2655931B1 - Multistep gear mechanism - Google Patents

Multistep gear mechanism Download PDF

Info

Publication number
EP2655931B1
EP2655931B1 EP11785413.3A EP11785413A EP2655931B1 EP 2655931 B1 EP2655931 B1 EP 2655931B1 EP 11785413 A EP11785413 A EP 11785413A EP 2655931 B1 EP2655931 B1 EP 2655931B1
Authority
EP
European Patent Office
Prior art keywords
shaft
planetary gear
gear
gear set
clutches
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP11785413.3A
Other languages
German (de)
French (fr)
Other versions
EP2655931A1 (en
Inventor
Gerhard Gumpoltsberger
Christian Sibla
Stefan Beck
Michael Wechs
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP2655931A1 publication Critical patent/EP2655931A1/en
Application granted granted Critical
Publication of EP2655931B1 publication Critical patent/EP2655931B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means

Definitions

  • the present invention relates to a planetary gear multi-speed transmission, in particular for a motor vehicle, according to the preamble of patent claim 1.
  • Multi-stage transmissions in planetary construction include in the prior art planetary gear sets, which are switched by means of friction or switching elements, such as clutches and brakes, and usually with a slipping action and optionally provided with a lock-up starting element, such as hydrodynamic torque converter or a fluid coupling, are connected.
  • friction or switching elements such as clutches and brakes
  • a lock-up starting element such as hydrodynamic torque converter or a fluid coupling
  • Such a multi-stage transmission planetary construction is for example from the DE 199 49 507 A1 known to the applicant;
  • two non-shiftable Vorschaltrad accounts are provided on the output side, the output side generate two speeds that are selectively switchable in addition to the speed of the drive shaft to a force acting on the output shaft, switchable Doppelplanetenradsatz by selectively closing the switching elements used that to switch from a gear in the respective next higher or lower gear from the two currently operated switching elements only one switching element must be switched on or off.
  • a 9-speed multi-speed transmission known; it comprises eight switching elements and four planetary gear sets, one planetary gear set serving as a primary gear and the main gear has a Simpson set and another serving as a reverse gear planetary gear.
  • the applicant is a planetary gear multi-speed transmission known which has a drive and an output, which are arranged in a housing.
  • the known transmission at least four planetary gear sets, hereinafter referred to as the first, second, third and fourth planetary gear set, at least eight rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft and at least six Switching elements, comprising brakes and clutches, provided, the selective intervention causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.
  • the first and the second planetary gear set which are preferably designed as negative planetary gear sets, that is to say with a negative stationary gear ratio, form a shiftable transfer gearset, the third and the fourth planetary gear set forming a main gearset.
  • the webs of the first and second planetary gear sets are coupled to each other via the fourth shaft, which is connected to an element of the main gearset that the ring gear of the first planetary gear set coupled to the sun gear of the second planetary gear via the eighth shaft is, which is detachably connectable via a first clutch to the drive shaft and that the sun gear of the first planetary gear set by means of the third shaft via a first brake to a housing of the transmission and releasably connectable via a second clutch to the drive shaft, wherein the ring gear of the second planetary gear set by means of the fifth shaft via a second brake to a housing of the transmission can be coupled.
  • the seventh shaft with at least one element of the main gearset is constantly connected and coupled via a third brake to the housing of the transmission
  • the sixth shaft is continuously connected to at least one further element of the main gear and releasably connected via a third clutch to the drive shaft
  • the output shaft is permanently connected to at least one further element of the main gearset.
  • the fourth shaft is constantly connected to the ring gear of the third planetary gear set, wherein the sixth shaft is continuously connected to the ring gear of the fourth planetary gear set and the web of the third planetary gear and releasably connectable via the third clutch to the drive shaft.
  • the seventh shaft is constantly connected to the sun gears of the third and fourth planetary gear set and can be coupled via the third brake to a housing of the transmission. The output takes place here via the output shaft permanently connected to the web of the fourth planetary gear set.
  • the third and the fourth planetary gear set may be combined or reduced to form a Ravigneaux set having a common web and a common ring gear.
  • the present invention has for its object to propose a multi-speed transmission of the type mentioned, which has at least nine forward gears and a reverse gear with sufficient translation, in which the construction cost and size, especially the overall length, or the weight can be optimized and also the efficiency is improved in terms of drag and gearing losses.
  • the multistage transmission according to the invention small supporting moments act on the shifting elements.
  • the transmission according to the invention should be suitable in particular for longitudinal installation but also for transverse installation in the vehicle.
  • a multi-speed transmission according to the invention is proposed in planetary construction, which has a drive and an output, which are arranged in a housing. Furthermore, at least four planetary gear sets, hereinafter referred to as first, second, third and fourth planetary gear set, nine rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh, eighth and ninth wave - and at least six Switching elements, comprising brakes and clutches, provided, the selective intervention causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.
  • first, second, third and fourth planetary gear set nine rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh, eighth and ninth wave - and at least six Switching elements, comprising brakes and clutches, provided, the selective intervention causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.
  • the planetary gear sets are preferably arranged axially in the order of the first planetary gearset, second planetary gearset, third planetary gearset, fourth planetary gearset or first planetary gearset, second planetary gearset, fourth planetary gearset, third planetary gearset, and are preferably configured as minus planetary gear sets.
  • the ring gear at a fixed web on a sun gear opposite direction of rotation.
  • a simple plus planetary gear includes a sun gear, a ring gear and a web on which inner and outer planetary gears are rotatably mounted, all inner planetary gears mesh with the sun gear and all outer planetary gears with the ring gear, each inner planetary gear, each with an outer Planet wheel meshes.
  • the ring gear has the same direction of rotation when the web is held on as the sun gear and there is a positive stationary gear ratio.
  • the sun gear of the first planetary gear set is connected to the fifth shaft, which is connected to the ring gear of the third planetary gear set and detachably connectable via a first clutch to the eighth shaft connected to the web of the second planetary gear set, which via a second clutch with the with the sun gear of the third planetary gear set and the sun gear of the fourth planetary gear set connected seventh shaft is detachably connectable.
  • the web of the first planetary gear set is connected to the drive shaft, which is connected to the ring gear of the second planetary gear set, wherein the sun gear of the second planetary gear set is connected to the ninth shaft, which is releasably connectable via a third clutch to the third shaft, which connected to the web of the third planetary gear set and can be coupled via a first brake to the housing of the transmission.
  • the ring gear of the fourth planetary gear set is connected to the fourth shaft, which is coupled via a second brake to the housing of the transmission, wherein the output shaft connected to the web of the fourth planetary gear set and via a fourth clutch with the with the ring gear of the first Planetenradsatzes connected sixth shaft is detachably connectable.
  • the inventive design of the multi-speed transmission results in particular for passenger cars suitable translations and increased total spread of the multi-speed transmission, whereby an improvement in ride comfort and a significant consumption reduction can be effected.
  • the construction cost is significantly reduced with the multi-stage transmission according to the invention by a small number of switching elements.
  • a switching element which is actuated in the first forward gear and in reverse is suitable.
  • the clutches and the brakes of the transmission can be designed as Reibschaltiata or lamellar switching elements, which have the advantage that they can be switched under load.
  • switching elements according to the invention can also be used as form-locking switching elements, such as synchronized or unsynchronized jaw clutches or brakes be formed.
  • a transmission according to the invention may comprise exclusively friction shifting elements or a combination of friction shifting elements and positive shifting elements. Positive locking switching elements are preferably used in places where this switching element can not be switched on under load, which may be the case for example in the starting gears or in very long translated high gears where a short interruption of traction due to the low Switzerlandkraftmakers tolerable without significant loss of comfort is. Due to the compact design of the transmission according to the invention, it is suitable both for a longitudinal installation as well as for a transverse installation in the vehicle.
  • the transmission according to the invention is designed such that an adaptability to different drive train configurations is made possible both in the power flow direction as well as in space.
  • FIG. 1 is a multi-stage transmission according to the invention with a drive shaft 1, an output shaft 2 and four planetary gear sets P1, P2, P3 and P4 shown, which are arranged in a housing G.
  • the planetary gear sets P1, P2, P3 and P4 are in the in FIG. 1 shown example designed as negative planetary gear sets.
  • at least one planetary gear set can be designed as a positive planetary gear set, if at the same time the web and Hohlradanulation exchanged and the amount of the stationary gear ratio is increased by 1 compared to the design as a minus planetary gear.
  • the planetary gear sets are arranged axially in the order P1, P2, P3, P4.
  • FIG. 1 how out FIG. 1 can be seen, six switching elements, namely two brakes 03, 04 and four clutches 26, 58, 39 and 78 are provided.
  • the spatial arrangement of the switching elements can be arbitrary and is limited only by the dimensions and the external shape.
  • the clutches and the brakes of the transmission are preferably designed as Reibschaltieri or lamellar switching elements.
  • the multi-speed transmission according to the invention has a total of nine rotatable shafts, namely the waves 1, 2, 3, 4, 5, 6, 7, 8 and 9, wherein the drive shaft forms the first shaft and the output shaft, the second shaft of the transmission.
  • the sun gear of the first planetary gear P1 is connected to the fifth shaft 5, which is connected to the ring gear of the third planetary gear set P3 and via a first clutch 58 with the connected to the web of the second planetary gear set P2 eighth shaft 8 is releasably connectable via a second clutch 78 with the sun gear of the third planetary gear set P3 and the sun gear of the fourth planetary gear set P4 connected seventh shaft 7 detachably is connectable.
  • the web of the first planetary gear P1 is connected to the drive shaft 1 of the transmission, which is connected to the ring gear of the second planetary P2; the sun gear of the second planetary gear set P2 is connected to the ninth shaft 9, which is detachably connectable via a third clutch 39 to the third shaft 3, which is connected to the web of the third planetary gear set P3 and a first brake 03 to the housing G of the transmission can be coupled.
  • the ring gear of the fourth planetary gear set P4 is connected to the fourth shaft 4, which is coupled via a second brake 04 to the housing G of the transmission, wherein the output shaft 2 connected to the web of the fourth planetary gear set P4 and a fourth clutch 26 with the connected to the ring gear of the first planetary gear set P1 sixth shaft 6 is detachably connectable.
  • the first and second brakes 03, 04 can be arranged axially next to each other.
  • the fourth clutch 26 and the second clutch 78 may preferably be disposed between the first planetary gear set P1 and the second planetary gear set P2.
  • FIG. 2 is an exemplary circuit diagram of a multi-speed transmission according to FIG. 1 shown. For each gear four switching elements are closed.
  • the shift scheme, the respective ratios i of the individual gear ratios and the gear ratios to be determined therefrom or increments ⁇ are taken to the next higher gear example, the value of 8,992 represents the spread of the transmission.
  • Typical values for the stationary gear ratios of the planetary gear sets P1, P2, P3 and P4 which are designed as minus planetary gear sets are respectively -2.292, -1.600, -1.600 and -2.449.
  • FIG. 2 It will be seen that in sequential switching mode only one switching element is switched on and one switching element has to be switched off, since two adjacent gear stages use three switching elements in common. Further, it will be seen that a large spread is achieved with small gear jumps.
  • the first forward gear is obtained by closing the first and second brakes 03, 04 and the second and third clutches 78, 39, the second forward gear by closing the second brake 04 and the first, second and third clutches 58, 78, 39, the third forward gear by closing the second brake 04 and the second, third and fourth clutches 78, 39, 26, the fourth forward gear by closing the second brake 04 and the first, second and fourth clutches 58, 78, 26, the fifth Forward gear by closing the second brake 04 and the first, third and fourth clutch 58, 39, 26, the executed as a direct gear sixth forward gear by closing all clutches 26, 39, 58, 78, the seventh forward gear by closing the first brake 03 and the first, third and fourth clutches 58, 39, 26, the eighth forward gear by closing the first brake 03 and the first, second and fourth clutches 58, 78, 26 and the ninth forward gear Gear is obtained by closing the first brake 03 and the second, third and fourth clutch 78, 39, 26, wherein the reverse gear by closing the first and second brake 03
  • an axle differential and / or a distributor differential can be arranged according to the invention.
  • the drive shaft 1 can be separated by a coupling element of a drive motor as needed, with a hydrodynamic converter, a hydraulic clutch, a dry starting clutch, a wet starting clutch, a magnetic powder clutch or a centrifugal clutch can be used as the coupling element. It is also possible to arrange such a starting element in the power flow direction behind the transmission, in which case the drive shaft 1 is constantly connected to the crankshaft of the drive motor.
  • the multistage transmission according to the invention also allows the arrangement of a torsional vibration damper between the drive motor and transmission.
  • a wear-free brake such. a hydraulic or electric retarder or the like, be arranged, which is particularly important for use in commercial vehicles of particular importance.
  • a power take-off may be provided to drive additional units on each shaft, preferably on the drive shaft 1 or the output shaft 2.
  • the friction shift elements used can be designed as power shift clutches or brakes.
  • non-positive clutches or brakes such as multi-plate clutches, band brakes and / or cone clutches can be used.
  • Another advantage of the multistage transmission presented here is that an electric machine can be mounted on each shaft as a generator and / or as an additional drive machine.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Description

Die vorliegende Erfindung betrifft ein Mehrstufengetriebe in Planetenbauweise, insbesondere für ein Kraftfahrzeug, gemäß dem Oberbegriff des Patentanspruchs 1.The present invention relates to a planetary gear multi-speed transmission, in particular for a motor vehicle, according to the preamble of patent claim 1.

Mehrstufengetriebe in Planetenbauweise, insbesondere für Kraftfahrzeuge, umfassen nach dem Stand der Technik Planetenradsätze, die mittels Reibungs- bzw. Schaltelementen, wie etwa Kupplungen und Bremsen, geschaltet werden und üblicherweise mit einem einer Schlupfwirkung unterliegenden und wahlweise mit einer Überbrückungskupplung versehenen Anfahrelement, wie etwa einem hydrodynamischen Drehmomentwandler oder einer Strömungskupplung, verbunden sind.Multi-stage transmissions in planetary construction, particularly for motor vehicles, include in the prior art planetary gear sets, which are switched by means of friction or switching elements, such as clutches and brakes, and usually with a slipping action and optionally provided with a lock-up starting element, such as hydrodynamic torque converter or a fluid coupling, are connected.

Ein derartiges Mehrstufengetriebe in Planetenbauweise ist beispielsweise aus der DE 199 49 507 A1 der Anmelderin bekannt; hierbei sind an der Antriebswelle zwei nicht schaltbare Vorschaltradsätze vorgesehen, die ausgangsseitig zwei Drehzahlen erzeugen, die neben der Drehzahl der Antriebswelle wahlweise auf einen auf die Abtriebswelle wirkenden, schaltbaren Doppelplanetenradsatz durch selektives Schließen der verwendeten Schaltelemente derart schaltbar sind, dass zum Umschalten von einem Gang in den jeweils nächstfolgenden höheren oder niedrigeren Gang von den beiden gerade betätigten Schaltelementen jeweils nur ein Schaltelement zu- oder abgeschaltet werden muss.Such a multi-stage transmission planetary construction is for example from the DE 199 49 507 A1 known to the applicant; Here, two non-shiftable Vorschaltradsätze are provided on the output side, the output side generate two speeds that are selectively switchable in addition to the speed of the drive shaft to a force acting on the output shaft, switchable Doppelplanetenradsatz by selectively closing the switching elements used that to switch from a gear in the respective next higher or lower gear from the two currently operated switching elements only one switching element must be switched on or off.

Unter Verwendung von fünf Schaltelementen werden hierbei sieben Vorwärtsgänge erzielt, unter Verwendung von sechs Schaltelementen neun oder zehn Vorwärtsgänge.Using five shifting elements, seven forward gears are achieved, with nine or ten forward gears using six shifting elements.

Ferner ist aus der DE 29 36 969 A1 ein 9-Gang-Mehrstufengetriebe bekannt; es umfasst acht Schaltelemente und vier Planetenradsätze, wobei ein Planetenradsatz als Vorschaltgetriebe dient und das Hauptgetriebe einen Simpson-Satz und einen weiteren als Umkehrgetriebe dienenden Planetenradsatz aufweist.Furthermore, from the DE 29 36 969 A1 a 9-speed multi-speed transmission known; it comprises eight switching elements and four planetary gear sets, one planetary gear set serving as a primary gear and the main gear has a Simpson set and another serving as a reverse gear planetary gear.

Weitere Mehrstufengetriebe sind beispielsweise aus der DE 102005 032 884 A1 DE 10 2005 010 210 A1 und der DE 10 2006 006 637 A1 der Anmelderin bekannt.Further multi-speed transmissions are for example from the DE 102005 032 884 A1 DE 10 2005 010 210 A1 and the DE 10 2006 006 637 A1 the applicant known.

Automatisch schaltbare Fahrzeuggetriebe in Planetenbauweise im Allgemeinen sind im Stand der Technik bereits vielfach beschrieben und unterliegen einer permanenten Weiterentwicklung und Verbesserung. So sollen diese Getriebe einen geringen Bauaufwand, insbesondere eine geringe Anzahl an Schaltelementen erfordern und bei sequentieller Schaltweise Doppelschaltungen, d.h. ein Zu- bzw. Abschalten von zwei Schaltelementen vermeiden, so dass bei Schaltungen in definierten Ganggruppen jeweils nur ein Schaltelement gewechselt wird.Automatically switchable vehicle transmissions in planetary construction in general are already widely described in the prior art and are subject to permanent development and improvement. Thus, these transmissions are to require a low construction cost, in particular a small number of switching elements and in sequential switching manner double circuits, i. avoid switching on or off of two switching elements, so that in circuits in defined gear groups only one switching element is changed.

Aus der DE 10 2008 000 428 A1 der Anmelderin ist ein Mehrstufengetriebe in Planetenbauweise bekannt, welches einen Antrieb und einen Abtrieb aufweist, welche in einem Gehäuse angeordnet sind. Bei dem bekannten Getriebe sind zumindest vier Planetenradsätze, im Folgenden als erster, zweiter, dritter und vierter Planetenradsatz bezeichnet, mindestens acht drehbare Wellen - im Folgenden als Antriebswelle, Abtriebswelle, dritte, vierte, fünfte, sechste, siebte und achte Welle bezeichnet sowie zumindest sechs Schaltelemente, umfassend Bremsen und Kupplungen, vorgesehen, deren selektives Eingreifen verschiedene Übersetzungsverhältnisse zwischen dem Antrieb und dem Abtrieb bewirkt, so dass vorzugsweise neun Vorwärtsgänge und ein Rückwärtsgang realisierbar sind.From the DE 10 2008 000 428 A1 The applicant is a planetary gear multi-speed transmission known which has a drive and an output, which are arranged in a housing. In the known transmission at least four planetary gear sets, hereinafter referred to as the first, second, third and fourth planetary gear set, at least eight rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft and at least six Switching elements, comprising brakes and clutches, provided, the selective intervention causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.

Hierbei bilden der erste und der zweite Planetenradsatz, die vorzugsweise als Minus-Planetenradsätze, also mit negativer Standgetriebe-Übersetzung, ausgebildet sind, einen schaltbaren Vorschaltradsatz, wobei der dritte und der vierte Planetenradsatz einen Hauptradsatz bilden.In this case, the first and the second planetary gear set, which are preferably designed as negative planetary gear sets, that is to say with a negative stationary gear ratio, form a shiftable transfer gearset, the third and the fourth planetary gear set forming a main gearset.

Bei dem bekannten Mehrstufengetriebe ist vorgesehen, dass die Stege des ersten und des zweiten Planetenradsatzes über die vierte Welle miteinander gekoppelt sind, welche mit einem Element des Hauptradsatzes verbunden ist, dass das Hohlrad des ersten Planetenradsatzes mit dem Sonnenrad des zweiten Planetenradsatzes über die achte Welle gekoppelt ist, welche über eine erste Kupplung mit der Antriebswelle lösbar verbindbar ist und dass das Sonnenrad des ersten Planetenradsatzes mittels der dritten Welle über eine erste Bremse an ein Gehäuse des Getriebes ankoppelbar und über eine zweite Kupplung mit der Antriebswelle lösbar verbindbar ist, wobei das Hohlrad des zweiten Planetenradsatzes mittels der fünften Welle über eine zweite Bremse an ein Gehäuse des Getriebes ankoppelbar ist. Zudem ist die siebte Welle mit zumindest einem Element des Hauptradsatzes ständig verbunden und über eine dritte Bremse an das Gehäuse des Getriebes ankoppelbar, wobei die sechste Welle mit zumindest einem weiteren Element des Hauptradsatzes ständig verbunden und über eine dritte Kupplung mit der Antriebswelle lösbar verbindbar ist; die Abtriebswelle ist mit zumindest einem weiteren Element des Hauptradsatzes ständig verbunden.In the known multi-speed transmission is provided that the webs of the first and second planetary gear sets are coupled to each other via the fourth shaft, which is connected to an element of the main gearset that the ring gear of the first planetary gear set coupled to the sun gear of the second planetary gear via the eighth shaft is, which is detachably connectable via a first clutch to the drive shaft and that the sun gear of the first planetary gear set by means of the third shaft via a first brake to a housing of the transmission and releasably connectable via a second clutch to the drive shaft, wherein the ring gear of the second planetary gear set by means of the fifth shaft via a second brake to a housing of the transmission can be coupled. In addition, the seventh shaft with at least one element of the main gearset is constantly connected and coupled via a third brake to the housing of the transmission, the sixth shaft is continuously connected to at least one further element of the main gear and releasably connected via a third clutch to the drive shaft; the output shaft is permanently connected to at least one further element of the main gearset.

Vorzugsweise ist bei dem bekannten Getriebe die vierte Welle ständig mit dem Hohlrad des dritten Planetenradsatzes verbunden, wobei die sechste Welle ständig mit dem Hohlrad des vierten Planetenradsatzes und dem Steg des dritten Planetenradsatzes verbunden und über die dritte Kupplung mit der Antriebswelle lösbar verbindbar ist. Ferner ist die siebte Welle ständig mit den Sonnenrädern des dritten und vierten Planetenradsatzes verbunden und über die dritte Bremse an ein Gehäuse des Getriebes ankoppelbar. Der Abtrieb erfolgt hierbei über die ständig mit dem Steg des vierten Planetenradsatzes verbundene Abtriebswelle. Des Weiteren können der dritte und der vierte Planetenradsatz zu einem Ravigneaux-Satz mit einem gemeinsamen Steg und einem gemeinsamen Hohlrad zusammengesetzt bzw. reduziert sein.Preferably, in the known transmission, the fourth shaft is constantly connected to the ring gear of the third planetary gear set, wherein the sixth shaft is continuously connected to the ring gear of the fourth planetary gear set and the web of the third planetary gear and releasably connectable via the third clutch to the drive shaft. Furthermore, the seventh shaft is constantly connected to the sun gears of the third and fourth planetary gear set and can be coupled via the third brake to a housing of the transmission. The output takes place here via the output shaft permanently connected to the web of the fourth planetary gear set. Furthermore, the third and the fourth planetary gear set may be combined or reduced to form a Ravigneaux set having a common web and a common ring gear.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, ein Mehrstufengetriebe der eingangs genannten Art vorzuschlagen, welches mindestens neun Vorwärtsgänge und einen Rückwärtsgang mit ausreichender Übersetzung aufweist, bei dem der Bauaufwand und die Baugröße, insbesondere die Baulänge, bzw. das Gewicht optimiert werden und zudem der Wirkungsgrad hinsichtlich der Schlepp- und Verzahnungsverluste verbessert wird. Zudem sollen bei dem erfindungsgemäßen Mehrstufengetriebe geringe Stützmomente auf die Schaltelemente wirken. Das erfindungsgemäße Getriebe soll insbesondere für einen Längseinbau aber auch für einen Quereinbau im Fahrzeug geeignet sein.The present invention has for its object to propose a multi-speed transmission of the type mentioned, which has at least nine forward gears and a reverse gear with sufficient translation, in which the construction cost and size, especially the overall length, or the weight can be optimized and also the efficiency is improved in terms of drag and gearing losses. In addition, in the multistage transmission according to the invention, small supporting moments act on the shifting elements. The transmission according to the invention should be suitable in particular for longitudinal installation but also for transverse installation in the vehicle.

Diese Aufgabe wird erfindungsgemäß durch die Merkmale des Patentanspruchs 1 gelöst. Weitere Vorteile und vorteilhafte Ausgestaltungen gehen aus den Unteransprüchen hervor.This object is achieved by the features of claim 1. Further advantages and advantageous embodiments will become apparent from the dependent claims.

Demnach wird ein erfindungsgemäßes Mehrstufengetriebe in Planetenbauweise vorgeschlagen, welches einen Antrieb und einen Abtrieb aufweist, welche in einem Gehäuse angeordnet sind. Des Weiteren sind zumindest vier Planetenradsätze, im Folgenden als erster, zweiter, dritter und vierter Planetenradsatz bezeichnet, neun drehbare Wellen - im Folgenden als Antriebswelle, Abtriebswelle, dritte, vierte, fünfte, sechste, siebte, achte und neunte Welle bezeichnet - sowie zumindest sechs Schaltelemente, umfassend Bremsen und Kupplungen, vorgesehen, deren selektives Eingreifen verschiedene Übersetzungsverhältnisse zwischen dem Antrieb und dem Abtrieb bewirkt, so dass vorzugsweise neun Vorwärtsgänge und ein Rückwärtsgang realisierbar sind.Accordingly, a multi-speed transmission according to the invention is proposed in planetary construction, which has a drive and an output, which are arranged in a housing. Furthermore, at least four planetary gear sets, hereinafter referred to as first, second, third and fourth planetary gear set, nine rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh, eighth and ninth wave - and at least six Switching elements, comprising brakes and clutches, provided, the selective intervention causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.

Die Planetenradsätze sind axial betrachtet vorzugsweise in der Reihenfolge erster Planetenradsatz, zweiter Planetenradsatz, dritter Planetenradsatz, vierter Planetenradsatz oder erster Planetenradsatz, zweiter Planetenradsatz, vierter Planetenradsatz, dritter Planetenradsatz angeordnet und sind vorzugsweise als Minus-Planetenradsätze ausgebildet.The planetary gear sets are preferably arranged axially in the order of the first planetary gearset, second planetary gearset, third planetary gearset, fourth planetary gearset or first planetary gearset, second planetary gearset, fourth planetary gearset, third planetary gearset, and are preferably configured as minus planetary gear sets.

Ein einfacher Minus-Planetenradsatz umfasst bekanntlich ein Sonnenrad, ein Hohlrad und einen Steg, an dem Planetenräder drehbar gelagert sind, die jeweils mit Sonnenrad und Hohlrad kämmen. Hierdurch weist das Hohlrad bei festgehaltenem Steg eine zum Sonnenrad entgegengesetzte Drehrichtung auf. Demgegenüber umfasst ein einfacher Plus-Planetenradsatz ein Sonnenrad, ein Hohlrad und einen Steg, an dem innere und äußere Planetenräder drehbar gelagert sind, wobei alle inneren Planetenräder mit dem Sonnenrad und alle äußeren Planetenräder mit dem Hohlrad kämmen, wobei jedes innere Planetenrad mit jeweils einem äußeren Planetenrad kämmt. Hierdurch weist das Hohlrad bei festgehaltenem Steg die gleiche Drehrichtung auf wie das Sonnenrad und es ergibt sich eine positive Standgetriebeübersetzung.A simple minus planetary gear known to include a sun gear, a ring gear and a ridge on which planet gears are rotatably mounted, each meshing with the sun gear and ring gear. In this way, the ring gear at a fixed web on a sun gear opposite direction of rotation. In contrast, a simple plus planetary gear includes a sun gear, a ring gear and a web on which inner and outer planetary gears are rotatably mounted, all inner planetary gears mesh with the sun gear and all outer planetary gears with the ring gear, each inner planetary gear, each with an outer Planet wheel meshes. As a result, the ring gear has the same direction of rotation when the web is held on as the sun gear and there is a positive stationary gear ratio.

Gemäß der Erfindung ist das Sonnenrad des ersten Planetenradsatzes mit der fünften Welle verbunden, die mit dem Hohlrad des dritten Planetenradsatzes verbunden und über eine erste Kupplung mit der mit dem Steg des zweiten Planetenradsatzes verbundenen achten Welle lösbar verbindbar ist, welche über eine zweite Kupplung mit der mit dem Sonnenrad des dritten Planetenradsatzes und dem Sonnenrad des vierten Planetenradsatzes verbundenen siebten Welle lösbar verbindbar ist.According to the invention, the sun gear of the first planetary gear set is connected to the fifth shaft, which is connected to the ring gear of the third planetary gear set and detachably connectable via a first clutch to the eighth shaft connected to the web of the second planetary gear set, which via a second clutch with the with the sun gear of the third planetary gear set and the sun gear of the fourth planetary gear set connected seventh shaft is detachably connectable.

Des Weiteren ist der Steg des ersten Planetenradsatzes mit der Antriebswelle verbunden, welche mit dem Hohlrad des zweiten Planetenradsatzes verbunden ist, wobei das Sonnenrad des zweiten Planetenradsatzes mit der neunten Welle verbunden ist, welche über eine dritte Kupplung mit der dritten Welle lösbar verbindbar ist, welche mit dem Steg des dritten Planetenradsatzes verbunden und über eine erste Bremse an das Gehäuse des Getriebes ankoppelbar ist.Furthermore, the web of the first planetary gear set is connected to the drive shaft, which is connected to the ring gear of the second planetary gear set, wherein the sun gear of the second planetary gear set is connected to the ninth shaft, which is releasably connectable via a third clutch to the third shaft, which connected to the web of the third planetary gear set and can be coupled via a first brake to the housing of the transmission.

Gemäß der Erfindung ist das Hohlrad des vierten Planetenradsatzes mit der vierten Welle verbunden, die über eine zweite Bremse an das Gehäuse des Getriebes ankoppelbar ist, wobei die Abtriebswelle mit dem Steg des vierten Planetenradsatzes verbunden und über eine vierte Kupplung mit der mit dem Hohlrad des ersten Planetenradsatzes verbundenen sechsten Welle lösbar verbindbar ist.According to the invention, the ring gear of the fourth planetary gear set is connected to the fourth shaft, which is coupled via a second brake to the housing of the transmission, wherein the output shaft connected to the web of the fourth planetary gear set and via a fourth clutch with the with the ring gear of the first Planetenradsatzes connected sixth shaft is detachably connectable.

Durch die erfindungsgemäße Ausgestaltung des Mehrstufengetriebes ergeben sich insbesondere für Personenkraftwagen geeignete Übersetzungen sowie eine erhöhte Gesamtspreizung des Mehrstufengetriebes, wodurch eine Verbesserung des Fahrkomforts und eine signifikante Verbrauchsabsenkung bewirkt werden.The inventive design of the multi-speed transmission results in particular for passenger cars suitable translations and increased total spread of the multi-speed transmission, whereby an improvement in ride comfort and a significant consumption reduction can be effected.

Darüber hinaus wird mit dem erfindungsgemäßen Mehrstufengetriebe durch eine geringe Anzahl an Schaltelementen der Bauaufwand erheblich reduziert. In vorteilhafter Weise ist es mit dem erfindungsgemäßen Mehrstufengetriebe möglich, ein Anfahren mit einem hydrodynamischen Wandler, einer externen Anfahrkupplung oder auch mit sonstigen geeigneten externen Anfahrelementen durchzuführen. Es ist auch denkbar, einen Anfahrvorgang mit einem im Getriebe integrierten Anfahrelement zu ermöglichen. Vorzugsweise eignet sich ein Schaltelement, welches im ersten Vorwärtsgang und im Rückwärtsgang betätigt wird.In addition, the construction cost is significantly reduced with the multi-stage transmission according to the invention by a small number of switching elements. Advantageously, it is possible with the multistage transmission according to the invention to carry out a start with a hydrodynamic converter, an external starting clutch or other suitable external starting elements. It is also conceivable to allow a starting operation with a start-up element integrated in the transmission. Preferably, a switching element which is actuated in the first forward gear and in reverse is suitable.

Des Weiteren ergibt sich bei dem erfindungsgemäßen Mehrstufengetriebe ein guter Wirkungsgrad in den Hauptfahrgängen bezüglich der Schlepp- und Verzahnungsverluste.Furthermore, in the multistage transmission according to the invention, a good efficiency in the main drives with respect to the drag and gear losses.

Ferner liegen geringe Drehmomente in den Schaltelementen und in den Planetenradsätzen des Mehrstufengetriebes vor, wodurch der Verschleiß bei dem Mehrstufengetriebe in vorteilhafter Weise reduziert wird. Zudem wird durch die geringen Drehmomente eine entsprechend geringe Dimensionierung ermöglicht, wodurch der benötigte Bauraum und die entsprechenden Kosten reduziert werden. Darüber hinaus liegen auch geringe Drehzahlen bei den Wellen, den Schaltelementen und den Planetenradsätzen vor.Furthermore, there are low torques in the switching elements and in the planetary gear sets of the multi-speed transmission, whereby the wear in the multi-speed transmission is advantageously reduced. In addition, a correspondingly small dimensioning is made possible by the low torques, whereby the required space and the corresponding costs are reduced. In addition, there are also low speeds at the shafts, the switching elements and the planetary gear sets.

Die Kupplungen und die Bremsen des Getriebes können als Reibschaltelemente bzw. Lamellenschaltelemente ausgeführt sein, die den Vorteil aufweisen, dass sie unter Last schaltbar sind. Schaltelemente im Sinne der Erfindung können jedoch auch als formschlüssige Schaltelemente wie z.B. synchronisierte oder unsynchronisierte Klauenkupplungen oder -bremsen ausgebildet sein. Ein erfindungsgemäßes Getriebe kann dabei ausschließlich Reibschaltelemente oder eine Kombination von Reibschaltelementen und formschlüssigen Schaltelementen umfassen. Formschlüssige Schaltelemente werden dabei vorzugsweise an Stellen eingesetzt, bei denen dieses Schaltelement nicht unter Last zugeschaltet können werden muss, was beispielsweise in den Anfahrgängen der Fall sein kann oder in sehr lang übersetzten hohen Gängen bei denen eine kurze Zugkraftunterbrechung aufgrund des geringen Zugkraftniveaus ohne merkliche Komforteinbußen tolerierbar ist. Aufgrund der kompakten Bauform des erfindungsgemäßen Getriebes ist es sowohl für einen Längseinbau als auch für einen Quereinbau im Fahrzeug geeignet.The clutches and the brakes of the transmission can be designed as Reibschaltelemente or lamellar switching elements, which have the advantage that they can be switched under load. However, switching elements according to the invention can also be used as form-locking switching elements, such as synchronized or unsynchronized jaw clutches or brakes be formed. A transmission according to the invention may comprise exclusively friction shifting elements or a combination of friction shifting elements and positive shifting elements. Positive locking switching elements are preferably used in places where this switching element can not be switched on under load, which may be the case for example in the starting gears or in very long translated high gears where a short interruption of traction due to the low Zugkraftniveaus tolerable without significant loss of comfort is. Due to the compact design of the transmission according to the invention, it is suitable both for a longitudinal installation as well as for a transverse installation in the vehicle.

Außerdem ist das erfindungsgemäße Getriebe derart konzipiert, dass eine Anpassbarkeit an unterschiedliche Triebstrangausgestaltungen sowohl in Kraftflussrichtung als auch in räumlicher Hinsicht ermöglicht wird.In addition, the transmission according to the invention is designed such that an adaptability to different drive train configurations is made possible both in the power flow direction as well as in space.

Die Erfindung wird im Folgenden anhand der beigefügten Figuren beispielhaft näher erläutert. In diesen stellen dar:

Figur 1:
Eine schematische Ansicht einer bevorzugten Ausführungsform eines erfindungsgemäßen Mehrstufengetriebes; und
Figur 2:
Ein beispielhaftes Schaltschema für ein Mehrstufengetriebe gemäß Figur 1.
The invention will be explained in more detail below by way of example with reference to the attached figures. These are:
FIG. 1:
A schematic view of a preferred embodiment of a multi-speed transmission according to the invention; and
FIG. 2:
An exemplary circuit diagram for a multi-speed transmission according to FIG. 1 ,

In Figur 1 ist ein erfindungsgemäßes Mehrstufengetriebe mit einer Antriebswelle 1, einer Abtriebswelle 2 und vier Planetenradsätzen P1, P2, P3 und P4 dargestellt, welche in einem Gehäuse G angeordnet sind. Die Planetenradsätze P1, P2, P3 und P4 sind bei dem in Figur 1 gezeigten Beispiel als Minus-Planetenradsätze ausgebildet. Gemäß der Erfindung kann zumindest ein Planetenradsatz als Plus-Planetenradsatz ausgeführt sein, wenn gleichzeitig die Steg- und Hohlradanbindung getauscht und der Betrag der Standgetriebeübersetzung im Vergleich zu der Ausführung als Minus-Planetenradsatz um 1 erhöht wird.In FIG. 1 is a multi-stage transmission according to the invention with a drive shaft 1, an output shaft 2 and four planetary gear sets P1, P2, P3 and P4 shown, which are arranged in a housing G. The planetary gear sets P1, P2, P3 and P4 are in the in FIG. 1 shown example designed as negative planetary gear sets. According to the invention, at least one planetary gear set can be designed as a positive planetary gear set, if at the same time the web and Hohlradanbindung exchanged and the amount of the stationary gear ratio is increased by 1 compared to the design as a minus planetary gear.

Bei dem gezeigten Ausführungsbeispiel sind die Planetenradsätze axial betrachtet in der Reihenfolge P1, P2, P3, P4 angeordnet.In the embodiment shown, the planetary gear sets are arranged axially in the order P1, P2, P3, P4.

Wie aus Figur 1 ersichtlich, sind sechs Schaltelemente, nämlich zwei Bremsen 03, 04 und vier Kupplungen 26, 58, 39 und 78 vorgesehen. Die räumliche Anordnung der Schaltelemente kann beliebig sein und wird nur durch die Abmessungen und die äußere Formgebung begrenzt. Die Kupplungen und die Bremsen des Getriebes sind vorzugsweise als Reibschaltelemente bzw. Lamellenschaltelemente ausgeführt.How out FIG. 1 can be seen, six switching elements, namely two brakes 03, 04 and four clutches 26, 58, 39 and 78 are provided. The spatial arrangement of the switching elements can be arbitrary and is limited only by the dimensions and the external shape. The clutches and the brakes of the transmission are preferably designed as Reibschaltelemente or lamellar switching elements.

Mit diesen Schaltelementen ist ein selektives Schalten von neun Vorwärtsgängen und einem Rückwärtsgang realisierbar. Das erfindungsgemäße Mehrstufengetriebe weist insgesamt neun drehbare Wellen auf, nämlich die Wellen 1, 2, 3, 4, 5, 6, 7, 8 und 9, wobei die Antriebswelle die erste Welle und die Abtriebswelle die zweite Welle des Getriebes bildet.With these switching elements a selective switching of nine forward gears and one reverse gear can be realized. The multi-speed transmission according to the invention has a total of nine rotatable shafts, namely the waves 1, 2, 3, 4, 5, 6, 7, 8 and 9, wherein the drive shaft forms the first shaft and the output shaft, the second shaft of the transmission.

Erfindungsgemäß ist bei dem Mehrstufengetriebe gemäß Figur 1 vorgesehen, dass das Sonnenrad des ersten Planetenradsatzes P1 mit der fünften Welle 5 verbunden ist, welche mit dem Hohlrad des dritten Planetenradsatzes P3 verbunden und über eine erste Kupplung 58 mit der mit dem Steg des zweiten Planetenradsatzes P2 verbundenen achten Welle 8 lösbar verbindbar ist, die über eine zweite Kupplung 78 mit der mit dem Sonnenrad des dritten Planetenradsatzes P3 und dem Sonnenrad des vierten Planetenradsatzes P4 verbundenen siebten Welle 7 lösbar verbindbar ist.According to the invention in the multi-stage transmission according to FIG. 1 provided that the sun gear of the first planetary gear P1 is connected to the fifth shaft 5, which is connected to the ring gear of the third planetary gear set P3 and via a first clutch 58 with the connected to the web of the second planetary gear set P2 eighth shaft 8 is releasably connectable via a second clutch 78 with the sun gear of the third planetary gear set P3 and the sun gear of the fourth planetary gear set P4 connected seventh shaft 7 detachably is connectable.

Gemäß der Erfindung und bezugnehmend auf Figur 1 ist der Steg des ersten Planetenradsatzes P1 mit der Antriebswelle 1 des Getriebes verbunden, welche mit dem Hohlrad des zweiten Planetenradsatzes P2 verbunden ist; das Sonnenrad des zweiten Planetenradsatzes P2 ist mit der neunten Welle 9 verbunden, welche über eine dritte Kupplung 39 mit der dritten Welle 3 lösbar verbindbar ist, welche mit dem Steg des dritten Planetenradsatzes P3 verbunden und über eine erste Bremse 03 an das Gehäuse G des Getriebes ankoppelbar ist.According to the invention and referring to FIG. 1 the web of the first planetary gear P1 is connected to the drive shaft 1 of the transmission, which is connected to the ring gear of the second planetary P2; the sun gear of the second planetary gear set P2 is connected to the ninth shaft 9, which is detachably connectable via a third clutch 39 to the third shaft 3, which is connected to the web of the third planetary gear set P3 and a first brake 03 to the housing G of the transmission can be coupled.

Ferner ist das Hohlrad des vierten Planetenradsatzes P4 mit der vierten Welle 4 verbunden, die über eine zweite Bremse 04 an das Gehäuse G des Getriebes ankoppelbar ist, wobei die Abtriebswelle 2 mit dem Steg des vierten Planetenradsatzes P4 verbunden und über eine vierte Kupplung 26 mit der mit dem Hohlrad des ersten Planetenradsatzes P1 verbundenen sechsten Welle 6 lösbar verbindbar ist.Further, the ring gear of the fourth planetary gear set P4 is connected to the fourth shaft 4, which is coupled via a second brake 04 to the housing G of the transmission, wherein the output shaft 2 connected to the web of the fourth planetary gear set P4 and a fourth clutch 26 with the connected to the ring gear of the first planetary gear set P1 sixth shaft 6 is detachably connectable.

Die erste und die zweite Bremse 03, 04 können axial betrachtet nebeneinander angeordnet sein. Zudem können die vierte Kupplung 26 und die zweite Kupplung 78 axial betrachtet vorzugsweise zwischen dem ersten Planetenradsatz P1 und dem zweiten Planetenradsatz P2 angeordnet sein.The first and second brakes 03, 04 can be arranged axially next to each other. In addition, viewed axially, the fourth clutch 26 and the second clutch 78 may preferably be disposed between the first planetary gear set P1 and the second planetary gear set P2.

In Figur 2 ist ein beispielhaftes Schaltschema eines Mehrstufengetriebes gemäß Figur 1 dargestellt. Für jeden Gang werden vier Schaltelemente geschlossen. Dem Schaltschema können die jeweiligen Übersetzungen i der einzelnen Gangstufen und die daraus zu bestimmenden Gangsprünge bzw. Stufensprünge φ zum nächst höheren Gang beispielhaft entnommen werden, wobei der Wert 8,992 die Spreizung des Getriebes darstellt.In FIG. 2 is an exemplary circuit diagram of a multi-speed transmission according to FIG. 1 shown. For each gear four switching elements are closed. The shift scheme, the respective ratios i of the individual gear ratios and the gear ratios to be determined therefrom or increments φ are taken to the next higher gear example, the value of 8,992 represents the spread of the transmission.

Typische Werte für die Standgetriebeübersetzungen der als Minus-Planetenradsätze ausgeführten Planetenradsätze P1, P2, P3 und P4 sind jeweils -2,292, -1,600, -1,600 und -2,449. Aus Figur 2 wird ersichtlich, dass bei sequentieller Schaltweise jeweils nur ein Schaltelement zugeschaltet und ein Schaltelement abgeschaltet werden muss, da zwei benachbarte Gangstufen drei Schaltelemente gemeinsam benutzen. Ferner wird ersichtlich, dass eine große Spreizung bei kleinen Gangsprüngen erzielt wird.Typical values for the stationary gear ratios of the planetary gear sets P1, P2, P3 and P4 which are designed as minus planetary gear sets are respectively -2.292, -1.600, -1.600 and -2.449. Out FIG. 2 It will be seen that in sequential switching mode only one switching element is switched on and one switching element has to be switched off, since two adjacent gear stages use three switching elements in common. Further, it will be seen that a large spread is achieved with small gear jumps.

Der erste Vorwärts-Gang ergibt sich durch Schließen der ersten und zweiten Bremse 03, 04 und der zweiten und dritten Kupplung 78, 39, der zweite VorwärtsGang durch Schließen der zweiten Bremse 04 und der ersten, zweiten und dritten Kupplung 58, 78, 39, der dritte Vorwärts-Gang durch Schließen der zweiten Bremse 04 und der zweiten, dritten und vierten Kupplung 78, 39, 26, der vierte VorwärtsGang durch Schließen der zweiten Bremse 04 und der ersten, zweiten und vierten Kupplung 58, 78, 26, der fünfte Vorwärts-Gang durch Schließen der zweiten Bremse 04 und der ersten, dritten und vierten Kupplung 58, 39, 26, der als Direktgang ausgeführte sechste Vorwärts-Gang durch Schließen sämtlicher Kupplungen 26, 39, 58, 78, der siebte Vorwärts-Gang durch Schließen der ersten Bremse 03 und der ersten, dritten und vierten Kupplung 58, 39, 26, der achte Vorwärts-Gang durch Schließen der ersten Bremse 03 und der ersten, zweiten und vierten Kupplung 58, 78, 26 und der neunte Vorwärts-Gang ergibt sich durch Schließen der ersten Bremse 03 und der zweiten, dritten und vierten Kupplung 78, 39, 26, wobei sich der Rückwärtsgang durch Schließen der ersten und zweiten Bremse 03, 04 und der ersten und dritten Kupplung 58, 39 ergibt.The first forward gear is obtained by closing the first and second brakes 03, 04 and the second and third clutches 78, 39, the second forward gear by closing the second brake 04 and the first, second and third clutches 58, 78, 39, the third forward gear by closing the second brake 04 and the second, third and fourth clutches 78, 39, 26, the fourth forward gear by closing the second brake 04 and the first, second and fourth clutches 58, 78, 26, the fifth Forward gear by closing the second brake 04 and the first, third and fourth clutch 58, 39, 26, the executed as a direct gear sixth forward gear by closing all clutches 26, 39, 58, 78, the seventh forward gear by closing the first brake 03 and the first, third and fourth clutches 58, 39, 26, the eighth forward gear by closing the first brake 03 and the first, second and fourth clutches 58, 78, 26 and the ninth forward gear Gear is obtained by closing the first brake 03 and the second, third and fourth clutch 78, 39, 26, wherein the reverse gear by closing the first and second brake 03, 04 and the first and third clutch 58, 39 results.

Dadurch, dass im ersten Vorwärtsgang und im ersten Rückwärtsgang die erste und zweite Bremse 03, 04 und die dritte Kupplung 39 geschlossen sind, können diese Schaltelemente als Anfahrelemente eingesetzt werden.Characterized in that in the first forward gear and in the first reverse gear, the first and second brake 03, 04 and the third clutch 39 are closed, these switching elements can be used as starting elements.

Gemäß der Erfindung ergeben sich auch bei gleichem Getriebeschema je nach Schaltlogik unterschiedliche Gangsprünge, so dass eine anwendungs- bzw. fahrzeugspezifische Variation ermöglicht wird.According to the invention, even with the same transmission scheme depending on the switching logic different gear jumps, so that an application or vehicle-specific variation is possible.

Erfindungsgemäß ist es möglich, an jeder geeigneten Stelle des Mehrstufengetriebes zusätzliche Freiläufe vorzusehen, beispielsweise zwischen einer Welle und dem Gehäuse oder um zwei Wellen gegebenenfalls zu verbinden.According to the invention, it is possible to provide additional freewheels at any suitable location of the multi-speed transmission, for example between a shaft and the housing or, if necessary, to connect two shafts.

Auf der Antriebsseite oder auf der Abtriebsseite können erfindungsgemäß ein Achsdifferential und/oder ein Verteilerdifferential angeordnet werden.On the drive side or on the output side, an axle differential and / or a distributor differential can be arranged according to the invention.

Im Rahmen einer vorteilhaften Weiterbildung kann die Antriebswelle 1 durch ein Kupplungselement von einem Antriebsmotor nach Bedarf getrennt werden, wobei als Kupplungselement ein hydrodynamischer Wandler, eine hydraulische Kupplung, eine trockene Anfahrkupplung, eine nasse Anfahrkupplung, eine Magnetpulverkupplung oder eine Fliehkraftkupplung einsetzbar sind. Es ist auch möglich, ein derartiges Anfahrelement in Kraftflussrichtung hinter dem Getriebe anzuordnen, wobei in diesem Fall die Antriebswelle 1 ständig mit der Kurbelwelle des Antriebsmotors verbunden ist.In the context of an advantageous development, the drive shaft 1 can be separated by a coupling element of a drive motor as needed, with a hydrodynamic converter, a hydraulic clutch, a dry starting clutch, a wet starting clutch, a magnetic powder clutch or a centrifugal clutch can be used as the coupling element. It is also possible to arrange such a starting element in the power flow direction behind the transmission, in which case the drive shaft 1 is constantly connected to the crankshaft of the drive motor.

Das erfindungsgemäße Mehrstufengetriebe ermöglicht außerdem die Anordnung eines Torsionsschwingungsdämpfers zwischen Antriebsmotor und Getriebe.The multistage transmission according to the invention also allows the arrangement of a torsional vibration damper between the drive motor and transmission.

Im Rahmen einer weiteren, nicht dargestellten Ausführungsform der Erfindung kann auf jeder Welle, bevorzugt auf der Antriebswelle 1 oder der Abtriebswelle 2, eine verschleißfreie Bremse, wie z.B. ein hydraulischer oder elektrischer Retarder oder dergleichen, angeordnet sein, was insbesondere für den Einsatz in Nutzkraftfahrzeugen von besonderer Bedeutung ist. Des Weiteren kann zum Antrieb von zusätzlichen Aggregaten auf jeder Welle, bevorzugt auf der Antriebswelle 1 oder der Abtriebswelle 2, ein Nebenabtrieb vorgesehen sein.In a further, not shown embodiment of the invention, on each shaft, preferably on the drive shaft 1 or the output shaft 2, a wear-free brake, such. a hydraulic or electric retarder or the like, be arranged, which is particularly important for use in commercial vehicles of particular importance. Furthermore, to drive additional units on each shaft, preferably on the drive shaft 1 or the output shaft 2, a power take-off may be provided.

Die eingesetzten Reibschaltelemente können als lastschaltbare Kupplungen oder Bremsen ausgebildet sein. Insbesondere können kraftschlüssige Kupplungen oder Bremsen, wie z.B. Lamellenkupplungen, Bandbremsen und/oder Konuskupplungen, verwendet werden.The friction shift elements used can be designed as power shift clutches or brakes. In particular, non-positive clutches or brakes, such as multi-plate clutches, band brakes and / or cone clutches can be used.

Ein weiterer Vorteil des hier vorgestellten Mehrstufengetriebes besteht darin, dass auf jeder Welle als Generator und/oder als zusätzliche Antriebsmaschine eine elektrische Maschine anbringbar ist.Another advantage of the multistage transmission presented here is that an electric machine can be mounted on each shaft as a generator and / or as an additional drive machine.

Bezugszeichenreference numeral

11
erste Welle, Antriebswellefirst shaft, drive shaft
22
zweite Welle, Abtriebswellesecond shaft, output shaft
33
dritte Wellethird wave
44
vierte Wellefourth wave
55
fünfte Wellefifth wave
66
sechste Wellesixth wave
77
siebte Welleseventh wave
88th
achte Welleeighth wave
99
neunte Welleninth wave
0303
erste Bremsefirst brake
0404
zweite Bremsesecond brake
2626
vierte Kupplungfourth clutch
3939
dritte Kupplungthird clutch
5858
erste Kupplungfirst clutch
7878
zweite Kupplungsecond clutch
P1P1
erster Planetenradsatzfirst planetary gear set
P2P2
zweiter Planetenradsatzsecond planetary gear set
P3P3
dritter Planetenradsatzthird planetary gear set
P4P4
vierter Planetenradsatzfourth planetary gear set
ii
Übersetzungtranslation
φφ
Stufensprungincrement
GG
Gehäusecasing

Claims (4)

  1. Multi-stage gearbox of planetary construction, in particular for a motor vehicle, having a drive input shaft (1), a drive output shaft (2), a housing (G), a first planetary gear set (P1), a second planetary gear set (P2), a third planetary gear set (P3) and a fourth planetary gear set (P4), wherein the planetary gear sets each comprise a sun gear, a web and an internal gear, having multiple rotatable shafts (1, 2, 3, 4, 5, 6, 7, 8, 9) and multiple shift elements (03, 04, 26, 39, 58, 78), comprising brakes (03, 04) and clutches (26, 39, 58, 78), the selective engagement of which generates different transmission ratios between the drive input shaft (1) and the drive output shaft (2), wherein the sun gear of the first planetary gear set (P1) is connected to a fifth shaft (5), which fifth shaft is connected to the internal gear of the third planetary gear set (P3) and is detachably connectable by means of a first clutch (58) to an eighth shaft (8), which eighth shaft is connected to the web of the second planetary gear set (P2) and is detachably connectable by means of a second clutch (78) to a seventh shaft (7), which seventh shaft is connected to the sun gear of the third planetary gear set (P3) and to the sun gear of the fourth planetary gear set (P4), wherein the web of the first planetary gear set (P1) is connected to the drive input shaft (1), which drive input shaft is connected to the internal gear of the second planetary gear set (P2), wherein the sun gear of the second planetary gear set (P2) is connected to a ninth shaft (9), which ninth shaft is detachably connectable by means of a third clutch (39) to a third shaft (3), which third shaft is connected to the web of the third planetary gear set (P3) and can be coupled by means of a first brake (03) to the housing (G) of the gearbox, wherein the internal gear of the fourth planetary gear set (P4) is connected to a fourth shaft (4), which fourth shaft can be coupled by means of a second brake (04) to the housing (G) of the gearbox, and wherein the drive output shaft (2) is connected to the web of the fourth planetary gear set (P4) and is detachably connectable by means of a fourth clutch (26) to a sixth shaft (6), which sixth shaft is connected to the internal gear of the first planetary gear set (P1).
  2. Multi-stage gearbox according to Claim 1, characterized in that nine rotatable shafts and six shift elements, specifically two brakes (03, 04) and four clutches (26, 39, 58, 78), are provided.
  3. Multi-stage gearbox according to Claim 1 or 2, characterized in that the planetary gear sets (P1, P2, P3, P4) are configured as minus planetary gear sets.
  4. Multi-stage gearbox according to one of Claims 1 to 3, characterized in that nine forward gears and one reverse gear can be engaged, wherein the first forward gear is generated by closing the first and second brakes (03, 04) and the second and third clutches (78, 39), the second forward gear is generated by closing the second brake (04) and the first, second and third clutches (58, 78, 39), the third forward gear is generated by closing the second brake (04) and the second, third and fourth clutches (78, 39, 26), the fourth forward gear is generated by closing the second brake (04) and the first, second and fourth clutches (58, 78, 26), the fifth forward gear is generated by closing the second brake (04) and the first, third and fourth clutches (58, 39, 26), the sixth forward gear is generated by closing all of the clutches (26, 39, 58, 78), the seventh forward gear is generated by closing the first brake (03) and the first, third and fourth clutches (58, 39, 26), the eighth forward gear is generated by closing the first brake (03) and the first, second and fourth clutches (58, 78, 26), and in that the ninth forward gear is generated by closing the first brake (03) and the second, third and fourth clutches (78, 39, 26), wherein the reverse gear is generated by closing the first and second brakes (03, 04) and the first and third clutches (58, 39).
EP11785413.3A 2010-12-21 2011-11-21 Multistep gear mechanism Not-in-force EP2655931B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010063670A DE102010063670A1 (en) 2010-12-21 2010-12-21 Multi-speed transmission
PCT/EP2011/070517 WO2012084373A1 (en) 2010-12-21 2011-11-21 Multistep gear mechanism

Publications (2)

Publication Number Publication Date
EP2655931A1 EP2655931A1 (en) 2013-10-30
EP2655931B1 true EP2655931B1 (en) 2014-12-24

Family

ID=45001753

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11785413.3A Not-in-force EP2655931B1 (en) 2010-12-21 2011-11-21 Multistep gear mechanism

Country Status (6)

Country Link
US (1) US8894536B2 (en)
EP (1) EP2655931B1 (en)
JP (1) JP5756864B2 (en)
CN (1) CN103270340B (en)
DE (1) DE102010063670A1 (en)
WO (1) WO2012084373A1 (en)

Families Citing this family (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8834313B2 (en) * 2012-09-14 2014-09-16 Ford Global Technologies, Llc Multiple speed transmission and method of operation
US9458914B2 (en) 2013-03-28 2016-10-04 Aisin Aw Co., Ltd. Automatic transmission
US9279478B2 (en) * 2014-03-07 2016-03-08 Gm Global Technology Operations, Llc Multi-speed transmission
DE102014213690A1 (en) * 2014-07-15 2016-01-21 Zf Friedrichshafen Ag transmission
KR101703583B1 (en) 2015-05-13 2017-02-07 현대자동차 주식회사 Planetary gear train of automatic transmission for vehicles
KR101703584B1 (en) * 2015-05-13 2017-02-07 현대자동차 주식회사 Planetary gear train of automatic transmission for vehicles
KR101724851B1 (en) * 2015-06-08 2017-04-10 현대자동차주식회사 Multy stage transmmission for vehicle
EP3347622B1 (en) * 2015-09-09 2021-01-27 Allison Transmission, Inc. Multi-speed transmission
KR101765604B1 (en) * 2015-09-14 2017-08-07 현대자동차 주식회사 Planetary gear train of automatic transmission for vehicles
US10072735B2 (en) 2016-09-28 2018-09-11 Allison Transmission, Inc. Multi-speed planetary transmission
US10161486B2 (en) 2016-09-28 2018-12-25 Allison Transmission, Inc. Multi-speed planetary transmission
US10473190B2 (en) 2016-09-28 2019-11-12 Allison Transmission, Inc. Multi-speed planetary transmission
US10072736B2 (en) 2016-09-28 2018-09-11 Allison Transmission, Inc. Multi-speed planetary transmission
US9933045B1 (en) 2016-09-28 2018-04-03 Allison Transmission, Inc. Multi-speed planetary transmission
US10316940B2 (en) 2016-09-28 2019-06-11 Allison Transmission, Inc. Multi-speed planetary transmission
US10060511B2 (en) 2016-09-28 2018-08-28 Allison Transmission, Inc. Multi-speed planetary transmission
US10161484B2 (en) 2016-09-28 2018-12-25 Allison Transmission, Inc. Multi-speed planetary transmission
US10364867B2 (en) 2016-09-28 2019-07-30 Allison Transmission, Inc. Multi-speed planetary transmission
US10302173B2 (en) 2016-09-28 2019-05-28 Allison Transmission, Inc. Multi-speed planetary transmission
US10156283B2 (en) 2016-09-28 2018-12-18 Allison Transmission, Inc. Multi-speed planetary transmission
US10253850B2 (en) 2016-09-28 2019-04-09 Allison Transmission, Inc. Multi-speed planetary transmission
US10174814B2 (en) 2016-09-28 2019-01-08 Allison Transmission, Inc. Multi-speed planetary transmission
US10260599B2 (en) * 2016-09-28 2019-04-16 Allison Transmission, Inc. Multi-speed planetary transmission
US10451147B2 (en) 2016-09-28 2019-10-22 Allison Transmission, Inc. Multi-speed planetary transmission
US10060512B2 (en) 2016-09-28 2018-08-28 Allison Transmission, Inc. Multi-speed planetary transmission
US10234001B2 (en) 2016-09-28 2019-03-19 Allison Transmission, Inc. Multi-speed planetary transmission
US10323723B2 (en) 2016-09-28 2019-06-18 Allison Transmission, Inc. Multi-speed planetary transmission
US10533644B2 (en) 2016-09-28 2020-01-14 Allison Transmission, Inc. Multi-speed planetary transmission
US10323722B2 (en) 2016-09-28 2019-06-18 Allison Transmission, Inc. Multi-speed planetary transmission
CN109630627B (en) * 2018-12-13 2022-01-18 彭建新 Nine-speed automobile automatic transmission

Family Cites Families (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2936969A1 (en) 1979-09-13 1981-04-02 Daimler-Benz Ag, 7000 Stuttgart PLANETARY WHEEL CHANGE-GEARBOX WITH ONE ADDITIONAL AND ONE MAIN GEARBOX FOR VEHICLES
JP4345147B2 (en) 1999-07-29 2009-10-14 アイシン精機株式会社 Transmission
DE19949507B4 (en) 1999-10-14 2014-10-23 Zf Friedrichshafen Ag Multi-speed transmission
US7011597B2 (en) 2004-03-24 2006-03-14 General Motors Corporation Multi-speed transmission
DE102005010210A1 (en) 2005-03-05 2006-09-14 Zf Friedrichshafen Ag Multi-speed transmission
JP4270145B2 (en) 2005-03-23 2009-05-27 トヨタ自動車株式会社 Multi-speed transmission
US7341537B2 (en) 2005-05-25 2008-03-11 General Motors Corporation Multi-speed transmission
DE102005032884B4 (en) * 2005-07-14 2016-07-21 Zf Friedrichshafen Ag Multi-speed transmission
US7364527B2 (en) 2005-09-23 2008-04-29 General Motors Corporation Nine speed automatic transmission with six torque-transmitting mechanisms
DE102006006637B4 (en) 2006-02-14 2015-02-19 Zf Friedrichshafen Ag Multi-speed transmission
JP2008215407A (en) 2007-02-28 2008-09-18 Aisin Aw Co Ltd Automatic transmission for vehicle
DE102008015919B4 (en) 2007-03-29 2016-12-01 GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) Eight-speed transmission
US7993236B2 (en) 2007-04-19 2011-08-09 GM Global Technology Operations LLC Multi-speed transmission
US7524259B2 (en) 2007-05-04 2009-04-28 Gm Global Technology Operations, Inc. Wide ratio transmission with four planetary gear sets and four brakes
DE102007022776A1 (en) * 2007-05-15 2008-12-04 Zf Friedrichshafen Ag Multi-speed transmission
US7691022B2 (en) 2007-07-09 2010-04-06 Gm Global Technology Operations, Inc. 9-speed transmission
US7695398B2 (en) 2007-07-09 2010-04-13 Gm Global Technology Operations, Inc. 9-speed transmission
US7931559B2 (en) 2007-08-23 2011-04-26 GM Global Technology Operations LLC Multi-speed transmission
DE102007055808A1 (en) * 2007-12-14 2009-06-18 Zf Friedrichshafen Ag 10-speed automatic transmission
DE102008000428A1 (en) 2008-02-28 2009-09-03 Zf Friedrichshafen Ag Multi-speed transmission
JP2009270667A (en) * 2008-05-09 2009-11-19 Kyowa Metal Work Co Ltd Multistage shift planetary gear train
US8038566B2 (en) * 2009-02-13 2011-10-18 GM Global Technology Operations LLC Multi-speed transmission
US8177675B2 (en) * 2009-02-13 2012-05-15 GM Global Technology Operations LLC Multi-speed transmission
DE102009028710B4 (en) * 2009-08-20 2019-08-29 Zf Friedrichshafen Ag Multi-speed transmission
DE102009028705B4 (en) * 2009-08-20 2021-07-01 Zf Friedrichshafen Ag Multi-speed transmission
DE102009028674A1 (en) * 2009-08-20 2011-02-24 Zf Friedrichshafen Ag Multi-speed transmission
DE102009028714A1 (en) * 2009-08-20 2011-02-24 Zf Friedrichshafen Ag Multi-speed transmission
DE102009047278A1 (en) 2009-11-30 2011-06-01 Zf Friedrichshafen Ag Multistage planetary transmission i.e. automatic transmission, for motor vehicle e.g. passenger car, has shaft connected with ring gear of planetary gear set and coupled to housing by brake
DE102009047276A1 (en) * 2009-11-30 2011-06-01 Zf Friedrichshafen Ag Multistage planetary transmission i.e. automatic transmission, for e.g. passenger vehicle, has shaft connected with hollow wheel of planetary gear set and coupled to housing of gear drive over bracket
DE102009047277A1 (en) 2009-11-30 2011-06-01 Zf Friedrichshafen Ag Multi-speed transmission in planetary design, particularly automatic transmission for motor vehicle, has drive shaft, output shaft, four planetary gear sets arranged in housing, nine rotatable shafts and six switching elements
DE102009047768A1 (en) * 2009-12-10 2011-06-16 Zf Friedrichshafen Ag Multi-stage planetary gearbox i.e. automatic gearbox, for commercial motor vehicle i.e. passenger car, has drive shaft coupled to housing of drive, and planetary gear set interlocked by closing clutches

Also Published As

Publication number Publication date
EP2655931A1 (en) 2013-10-30
JP5756864B2 (en) 2015-07-29
DE102010063670A1 (en) 2012-06-21
US20130274058A1 (en) 2013-10-17
WO2012084373A1 (en) 2012-06-28
CN103270340A (en) 2013-08-28
US8894536B2 (en) 2014-11-25
CN103270340B (en) 2015-09-09
JP2014500460A (en) 2014-01-09

Similar Documents

Publication Publication Date Title
EP2655931B1 (en) Multistep gear mechanism
EP2655932B1 (en) Multistep gear mechanism
EP2467620B1 (en) Multi-ratio transmission
EP2467618B1 (en) Multi-ratio transmission
EP2467615B1 (en) Multi-ratio transmission
EP2467616B1 (en) Multi-ratio transmission
EP2467621B1 (en) Multi-ratio transmission
WO2012052284A1 (en) Multi-stage gearbox
WO2012052283A1 (en) Multi-stage gearbox
DE102010061402A1 (en) Multi-stage transmission for planetary construction, particularly automatic transmission for motor vehicle, comprises drive shaft, output shaft and four planetary gear sets, which are arranged in housing
DE102010042671A1 (en) Multi-speed transmission
DE102011084010A1 (en) Planetary-design multistage transmission i.e. automatic transmission, for passenger car, has shaft connected with bar of wheel set, output shaft connected with bar of another wheel set, and ring gear of former wheel set coupled to housing
DE102010039984A1 (en) Multi-stage planetary-type gearbox e.g. automatic gearbox, for passenger car, has planetary gear set whose bar is coupled to housing of gearbox via brake, where drive shaft, output shaft and three planetary gear sets are arranged in housing
WO2012084371A1 (en) Multi-speed gearbox
WO2012072392A1 (en) Multi-stage gearbox
DE102010039993A1 (en) Multi-step planetary gear box for motor vehicle, has planetary gear sets that are connected together via shafts, clutches and brakes, and drive and driven shafts connected to webs of planetary gear sets, respectively
DE102010040002A1 (en) Multistage gearbox, particularly automatic gearbox for motor vehicle, has drive shaft, output shaft and four planetary wheel sets, which are arranged in housing
DE102010039995A1 (en) Multistage gearbox, particularly automatic gearbox for motor vehicle, has drive shaft, output shaft and four planetary wheel sets, which are arranged in housing
WO2012052285A1 (en) Multi-stage gearbox
DE102010039998A1 (en) Multistage gearbox, particularly automatic gearbox for motor vehicle, has drive shaft, output shaft and four planetary wheel sets, which are arranged in housing
DE102010039990A1 (en) Multi-step planetary gear box for motor vehicle, has planetary gear sets that are connected together via shafts and clutches, and drive and driven shafts connected to webs of planetary gear sets, respectively
WO2012052286A1 (en) Multi-stage gearbox
DE102010039991A1 (en) Multi-stage planetary-type gearbox i.e. automatic gearbox, for passenger car, has planetary gear set whose sun gear is connected with shaft, which is coupled to housing via brake, where ring gear of planetary gear set is connected to shaft
DE102010039996A1 (en) Multi-step planetary reduction gearbox for motor vehicle, has planetary gear trains selectively engaged with shafts so that various transmission ratios are produced between drive and driven shafts to realize forward and reverse gears
DE102010040000A1 (en) Multi-step planetary gearbox for motor vehicle, has planetary gear trains that are selectively engaged with shafts so that various transmission ratios are produced between drive and driven shafts to realize forward and reverse gears

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20130516

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 502011005427

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F16H0003660000

Ipc: F16H0003620000

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: F16H 3/66 20060101ALI20140724BHEP

Ipc: F16H 3/62 20060101AFI20140724BHEP

INTG Intention to grant announced

Effective date: 20140813

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 703324

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150115

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502011005427

Country of ref document: DE

Effective date: 20150219

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20141224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150324

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150325

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150424

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011005427

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20150925

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151121

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20151121

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20151130

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20151130

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20160729

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20151121

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20151121

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20151130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20111121

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20151130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 703324

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161121

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161121

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141224

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20191105

Year of fee payment: 9

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502011005427

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210601